Cash register



Feb. 25, 1936. B SHIPLEY 2,031,860

CASH REGISTER Filed Jan. 24, 1939 14 Sheets-Sheet 1 FIG. 1

Cent

' Dollars MM Quinn H01 Bel-nil M. Shipley in. attain Feb. 25, 1936.

B. M. SHIPLEY 2,031,860

CASH REGISTER Filed Jan. 24, 19.30

FIG.2

l4 Sheets-Sheet 2 g 1 mm W01 Berni: M. Shipley H]. (100: nu q 5 M. SHIPLEY Feb. 25, 1936.

CASH REGISTER Filed Jan. 24, 193C) 14 Sheets-Sheet 3 III; I rlifl. lllllliflllfllv iltllIIllllliflldiillllullIIIIQIIIIIII!0!:Illiilltlll 4 awa J n ucntol Berni: M. Shipley ime 5 Rb alfeiuu B M. SHIPLEY Feb. 25, 1936.

CASH REGISTER Filed Jan. 24, 1953 14 Sheets-Sheet 4 FIG. 5

Berni: M. Shipley His B. M. SHIPLEY CASH REGISTER Feb. 25, 1936.

Filed Jan. 24, 1930 14 Sheets-Sheet 5 3 nuc'u 01; Berni: M. Shipley I GU10: 11m;

Feb. 25, 1936. B. M SHlPLEY 2,031,860

CASH REGISTER Filed Jan. 24, 1939 14 Sheets-Sheet 6 Snow 01,

Berni: M. Shipley y B. M. SHIPLEY Feb. 25, 1936.

CASH REGISTER Filed Jan. 24, 1930 14 Sheets-Sheet 7 P] ease Pay Cashir THE JOHN DOEDO.

DAYTOILOHIO [2)MAY 20 456 $2.70

gnuentoz Berni: M. Shiplcy MW FIG. 17

3 7 9 1452 469 MAYZU NUMBER N0 SALE RESET NUlgBER N S or o. THEJEHN $05 so.

CUSTOM ERS ReBislrN6t114 Totalhmount 10' His Qttoz nu B. M. SHIPLEY Feb. 25, 1936.

CASH REGISTER Filed Jan. 24, 1930 14 Sheets-Sheet 8 28 ass B. M. SHIPLEY Feb. 25, 1936.

CASH REGISTER Filed Jan. 24, 1930 14 Sheets-Sheet 9 Berni: M. Shipley Feb. 25, 1936. B $H|PLEY 2,031,860

CASH REGISTER Filed Jan. 24, 193C] 14 Sheets-Sheet l0 3/ 32 485 3 FIG.28 I 4 485 FIG. 29

Berni: M. Shipley B. M. SHIPLEY Feb. 25, 1936.

CASH REGISTER Filed Jan. 24, 1950 14 Sheets-Sheet 1 l 3 )1 new 1 for, Berni: M. Shipley Feb. 25, 1936. B. M, SHIPLEY CASH REGISTER Filed Jan. 24, 1930 14 Sheets-Sheet 12 Jnuani'oc Berni: M. Shipley Hi (forums Feb. 25, 1936. B. M. SHlPLEY 2,031,860

CASH REGISTER Filed Jan. 24, 1930 14 Sheets-Sheet 13 FIG. 39 4/ 33 a Q 0 9 g 32 a 0 1 I3 34 Z9 QI 0 FIG. 40

Jwuvntoc Berni: M. Shiplq 8' Mauve/W B. M. SHIPLEY CASH REGISTER Feb. 25, 1936.

Filed Jan. 24, 1930 14 Sheets-Sheet 14 Patented Feb. 25, 1936 UNITED STATES PATENT OFFICE National Cash Register Company,

Dayton,

Ohio, a corporation of Maryland Application January 24, 1930, Serial No. 423,230

31 Claims.

This invention relates to cash registers and like machines, and more particularly refers to improvements in machines of the press-down key type.

The machine of the present invention is an im proved and simplified machine of the type disclosed in United States Letters Patent No. 1,804,650, issued to Bernis M. Shipley on May 12, 1931, and in application for Letters Patent of the w United States, Serial No. 334,482, filed January 23,

1929, by Bernis M. Shipley.

The machine of the present application is characterized by its simple and inexpensive construction and ability to perform certain of the functions 15 usually found only in more expensive cash registers.

Heretofore, difllculty has been experienced in adapting the roller type indicator to machines of the press-down key type, due to whipping of the indicator which must be set at the downward stroke of the keys. This stroke is quite rapid and, when, for instance, the "9" key, or any of the higher order keys, are depressed with the suddenness peculiar to this type of machine, the in- 25 dicators, rotating rapidly from zero position and stopping suddenly in the 9" position or other higher order positions, throw a great strain on the indicators and on the indicatorsetting mechanism.

It is an object of the present invention to provide an inexpensive and simplified form of pressdown key type cash register, embodying receipt printing and total printing elements usually found only in more expensive machines.

Another object is to adapt the roller type of indication to a press-down key type machine.

Still another object of the present invention is to provide novel and improved indicator aligning mechanism.

40 with these and incidental objects in view the invention includes certain novel features of construction and combinations of parts, the essential elements of which are set forth in appended claims and a preferred form or embodiment of which is 4-3 hereinafter described with reference to the drawings which accompany and form a part of this specification.

In said drawings:

Fig. 1 is a. perspective view of the machine in- 50 cased in its cabinet.

Fig. 2 is a top plan view of the machine with the cabinet removed.

Fig. 3 is a transverse sectional view taken through the machine to the left Of the 80 key,

55 on line 3-3, Fig. 2.

Fig, 4 is a detail view of the positively operated overthrow preventor.

Fig. 5 is a perspective of one of the differential frames.

Fig. 6 is a top plan view of the check printing 5 types and setting mechanism.

Fig. 7 is a detail view of the indicator aliner operating mechanism and means for rotating the drive shaft.

Fig. 8 is a detail view of the means to prevent overthrow of the totalizer engaging cam. 0

Fig. 9 is a detail view of a part of the drive shaft operating mechanism. 7

Fig. 10 is a detail view of the clerk type wheels setting gear aligning mechanism. 1 5

Fig. 11 is a top plan view of the totalizer.

Fig. 12 is a view in left elevation of the receipt printer.

Fig. 13 is a detail view of the consecutive counter associated with the check printer.

Fig. 14 is a detail view in front elevation of the check severing device.

Fig. 15 is a detail view of the receipt or check printing hammer.

Fig. 16 is a fac-simile of the receipt issued by the machine.

Fig. 17 is a fac-simile of the total slip printed by the total printer.

Fig. 18 is a top plan view of the check printing hammer.

Fig. 19 is a detail view of the total printing hammer.

Fig. 20 is a detail view of the no sale counter and its operating mechanism.

Fig. 21 is a detail view in front elevation of the ribbon feeding and reversing mechanism.

Fig. 22 is a detail view of the check feed retaining pawls.

Fig, 23 is an enlarged detail view of the amount type wheel aliner and its operating mechanism.

Fig. 24 is an enlarged detail view of a part of the mechanism illustrated in Fig. 25.

Fig. 25 is a detail view of the check teed operating mechanism.

Fig. 26 is a fragmentary view of the paper tension device.

Fig. 27 is a. detail view partly in section. showing the details of construction of the check feed drive mechanism. 1

Fig. 28 is a top plan view of the type wheel line having mounted thereon a. reset counter, customer's counter, no sale counter, and date type wheel. Impressions are made from this type wheel line on the issuing total record strip.

Fig. 29 is a detail view of the customer counter and its operating mechanism therefor.

Fig. 30 is a sectional view taken on line 3il--3fl Fig. 28.

Fig. 31 is a sectional view of the reset counter operating means taken on line 3I--3|, Fig. 28.

Fig. 32 is a sectional view taken on line 32-42, Fig. 28.

Fig. 33 is a view in left elevation of the total resetting interlocks.

Fig. 34 is a detail view of the resetting operating levers.

Fig. 35 is a detail view of the resetting shaft retaining dog.

Fig. 36 is a fragmentary sectional view illustrating the method of mounting the resetting lever.

Fig. 3'7 is a view in elevation showing the mechanism for selectively locking the machine.

Fig. 38 is a fragmentary detail view of the spring pressed aliner and locating pawl for the machine lock control setting lever.

Fig. 39 is a perspective of the main frame work of the machine.

Fig. 40 is a view in front elevation of the back frame of the machine showing the arrangement of the key stops or locks.

Fig. 41 is a fragmentary detail view showing the spring for partially opening one of the lids or covers.

Fig. 42 is a perspective somewhat similar to Fig. 5, and showing the connections between the differential frames and the totalizer.

General description The main elements usually provided in cash registers of the type to which this application is drawn are included in the present machine. These elements include depressible keys, a totalizer, totalizer actuators and totalizer engaging and disengaging means, all driven by an operation of the keys. In addition, printing and feeding mechanism are provided to print and issue a receipt having printed thereon a clerks identification symbol, the date, consecutive number and the amount of the transaction entered.

Manually operated means is provided to print on a record strip, the total amount standing on the totalizer, a section of which strip may be drawn out and detached by the operator. The slip so detached contains a record of the total when the totalizer is reset to zero, or of a subtotal of periodic business. It also has printed thereon from another type line, the serial number of the resetting operation, the number of customers served, the number of no-sale operations and the date of the transaction.

Depression of an amount key, as is the case in most machines of the press-down key type, engages the totalizer with the actuator, operates the actuators to add amounts on the totalizer, and disengages the totalizer from the actuator. The keys, when depressed, also set indicators and type wheels and release the normally inaccessible cash drawer for operation.

Detailed description The main body of the machine is supported between two main side frames, at left side frame 29, and a right side frame 30 (Figs. 2, 3, 12, 18, 37 and 39), secured to opposite sides of a subbase 3i. The side frames 29 and 30 are connected at the rear by a wide channel bar 32, at their top by a cross bar 33, and at the front by a cross bar 34. The base 3i, in turn, is fastened to and supported on a framework 35 extending forwardly from the base and forming, in conjunction therewith, a closure suitable for accommodating a cash drawer 36, a fragment of which is shown in Fig. 37. A cabinet or casing 31 encloses the mechanism of the machine, the top of the cabinet being so shaped to form a suitable closure for indicators 33 (Fig. 3), supported on an indicator shaft 4 journaled in indicator frames Iii (Figs. 3 and 39), secured to the top of the side frames 29 and 3D and being joined at their tops by a cross bar 42. Suitable sight openings 43 (Fig. 3), in the cabinet 31, at the front and rear of the indicators shown, enable the indicators to be seen. The framework and the cabinet 31 rest on a base 33 (Figs. 1, 3 and 37).

Keyboard The keyboard selected for illustrative purposes includes three denominational groups of pressdown type amount keys, a group of amount keys 44, (Figs. 1, 2, 3, and 3'7) to register the units of cents, a group of amount keys 45 to register the tens of cents. and a group of keys 46 to register the units of dollars. A no-sale" key 41 is located at the extreme left of the keyboard (Figs. 1 and 2) to operate the machine when no amount is to be registered in the totalizer, but merely to gain access to the cash drawer.

All of the key levers are pivoted on a. supporting rod 43 (Fig. 3) extending between, and supported in, the side frames 28 and 30. The forward ends of the keys project through vertical guide slots 49 in the cabinet 31 and carry the usual designating key tops.

A key coupler 55 (Figs. 2, 3, '7, l2, 15, 25 and 3'7) cooperates with all of the key levers 44, 45, 46 and 41, to restore them to normal position after they have been fully depressed, and to actuate certain elements of the machine, as will be described later. The key coupler 55 extends across the machine in the rear of the support rod 48, just above the rear arms of the key levers, and rocks on pintles 5i) and 5| (Fig. 2)

projecting inwardly from the side frames 29 and 30 respectively. The lower edge of the key coupler 55 extends rearwardly to form a coupling bar 56 resting on the rear arms of the key levers and in line with recesses 51 formed in the enlarged rear arms of the key levers. key, or a key in each of the groups, is depressed, it rocks the key coupler upwardly, and, due to the key coupler and the key levers being pivoted on different centers, the coupling bar 56 enters the recesses 51 in the depressed keys, to couple 7,

these keys together. At the same time the coupling bar 56 passes upwardly in front of arcuate edges 54 on the forward part of the enlarged rear arms of the undepressed keys, thereby locking such keys against depression after the depressed key has been advanced a certain distance.

An interlock, comprising a plurality of key stops 53 (Figs. 3, 39 and 40) pivotally supported on the back frame 32 prevents depression of When a tions 52 for the remainder of the keys in the bank to prevent depression thereof.

When the operator releases the depressed key after it has been fully depressed, the weight of the key coupler 55 rocks the key or keys to normal position.

Diflerential mechanism A differentially movable element, similar to the differential mechanism disclosed in the above named patent of Bernis M. Shipley, No. 1,804,650, is associated with each denominational group of amount keys 44, 45 and 46.

A differential cam slot 58 is formed in the enlarged rear of each of the key levers, of each group of keys, to give the differential elements different extents of movement according to a particular key depressed in each group. In the tens of cents group (Fig. 3) depression of the key 45 engages its cam slot 58 with a universal rod 59 extending above the mouths of the cam slots 58 in the keys 45 and being carried between two segments 69 (Figs. 5 and 42), pivoted on a rod BI, extending between the side frames 29 and 39 of the machine, to rock the bail formed by the segments 59 and the rod 59, a distance corresponding to the value of the key depressed. The rod 59 is rotatably mounted on spindles (not shown) projecting inwardly from the lower end of the segments 59.

The rod 59 does not connect the segments 69 rigidly together, wherefore it is necessary to provide other means to insure uniform movement of these segments. When a depressed key cooperates with the universal rod 59 near one of its ends and its slot engages the rod 59 to advance the differential bail correspondingly, the segment 59 farthest from the depressed key has a tendency to lag, thereby causing torsional strain on the segment and on the rod 59. This strain is eliminated by a pair of pinions 52 (Figs. 5 and 42) fast on a shaft 53 joumaled in a pair of brackets and I5 secured to the machine side frames 29 and 39 respectively. the shaft 53 being parallel with the rod BI on which the segments 59 are journaled. For the sake of clearness, the shaft 59 and pinions 52 are shown in Fig. 5 below their correct positions; Figs. 3 and 42, however, show them correctly. The'pinions 62 mesh with the segments 89. .The rotary motion of one of the segments 59 is communicated by the pinions 52 and the shaft 59 to the other segment 59 to rotate this segment a distance exactly equal in extent of movement to the movement of its companion segment.

During its return movement the depressed key restores the differential bail to its normal position where its movement is arrested by a. toe 64 on the segment 89 striking a stud 55 (Fig. 3) projecting laterally from the rear arm of the Ill-cent key 45. The stud 55 stops the bail with the rod 59 in alignment with the mouths of the differential slots 58 in the rear arms of the key levers 45.

A zero stop arm (not shown) is provided in connection with each group of keys to prevent movement of the differential bail out of zero position when no key is depressed in that particular group. This zero stop arm is identical with the one disclosed in Shipleys application, Serial No. 334,482 and since it has no particular bearing on the present invention, detailed description thereof is omitted from this specification.

Referring to Fig. 42, a differential actuating mechanism comprising a pair of segments I9 and I99 and a universal rod I94 are provided to cooperate with the units-of-cents keys 44, and a pair of segments 11 and 18 and a universal rod I are provided to cooperate with the units-of-dollars keys 45. A pair of pinions 59 fast on a shaft 51 mesh with the segments 19 and I99 to synchronize their movement. Likewise, the segments TI and I9 are joined by a pair of pinions I21 on a shaft 58.

Additional pinions I93, one fast on each shaft 63 and 58, mesh with segments IBI and I92 respectively, journaled on the rod 5I. These segments, along with segment I99, set the type cariers corresponding to the particular key depressed in each of the groups of keys.

The movements of the differential elements are transmitted to the totalizers to accumulate thereon the amount corresponding in value to the particular keys 44, and 45 depressed.

This is accomplished for the group of tens-ofcents keys 45 by extending one of the segments 59 upwardly and toward the front of the machine to form a totalizer actuator segment 19. Likewise, the segment 79 of the units-of-cents differential bail I94 is extended to form a totalizer actuator segment H. In the case of the units-of-doilars bail I26, both differential segments are located out of line with the totalizer. To transmit the differential movement of the bail I25 to add on to the dollars totalizer wheel, a. pinion I2 fast on the shaft 58 meshes with a segment I28 pivotedon the rod 6i and is extended to form a totalizer actuator segment I3. Obviously the movement of the various differential bails, through the mechanism described, sets the totalizer actuators differentially according to the value of the keys depressed in the several groups.

Totalizer The totalizer illustrated in connection with the present invention is of the general type as disclosed in the patent to Thomas Carney, No. 532,762, issued January 22, 1895, and it is thought that a brief description of the totalizer will be sufficient.

The totalizer is not visible to the operator, and in order to ascertain the amount standing thereon it is necessary to take an impression, in a manner to be later described, on the record material from the totalizer wheels, which in the present instance are printing wheels.

The totalizer includes 2. units 01 cents wheel 99 (Fig. 11), a tens of cents wheel II, a units of dollars wheel 92 and a plurality of overflow wheels 59. The totalizer wheels 99, 9| and 92 are actuated by the units and tens of cents and the units of dollars actuators II, I9 and II, respectively,

which mesh with gears I4, one fast on each of the wheels 99, 9| and 82, and the lower order wheel 93. The wheels 93 are used to accumulate the overflow from the units of dollar wheels 92. The usual transfer or carrying over mechanism is provided for the wheels 99, 9i and 82 and the lowest order wheel 83 and the, conventional Geneva transfer, such as is disclosed in the abovementioned Carney patent, is provided for the higher order overflow wheels 93.

The totalizer wheels are all rotatably mounted on a shaft 84 jcurnaled in totalizer side frames 85 and 95, which in turn are rcckably mounted on pinties, only one of which 81 is shown herein. extending inwardly from a pair of intermediate frames 99 (Figs. 33 and 39) and 99 (Figs. 3 and 39), suitably supported in the machine on the cross bars 33, 34, and on the rod H. The totalizer side frames and 95 are Joined at their tops by an electro support bar 99 and at their Til Iii)

forward edges by a bar 9I having its ends bent, and secured to the frames 85 and 86. The bar 9| supports a part of the transfer mechanism (not shown) with which the totalizer is provided and also forms a convenient support for a looking device to be described later. The lower end of the totalizer frame 05 forms a bell crank comprising two arms 92 and 93 extending forwardl therefrom and carrying rollers 94 and 95 respectively, cooperating with a pair of cams 96 and 91 (see also Fig. 8), rotatably mounted on a shaft 98 journaled in the intermediate frames 08 and 09. The earns 96 and 91 receive one-half of one rotation in a counter-clockwise direction as viewed in Figs. 3 and 8, by mechanism, to be described later, to rock the totalizer frames 85 and 86 first counter-clockwise to carry the totalizer wheels into mesh with the totalizer actuators and then, after the amount has been added on the totalizer, rocks the totalizer out of mesh with the acuators before said actuators return to their normal positions.

The totalizer is rocked into engagement with the actuators at the very beginning of the down stroke of the keys, there being a brief time before the cam slot 50 in the rear arm of the depressed key engages the rod 59 for this purpose, and is disengaged from the actuator at the end of the downward stroke of the key. A dwell near the bottom of the cam slot 56 allows for the disengaging of the totalizer as the key approaches the limit of its downward stroke.

After the totalizer is disengaged from the actuators, the operator releases the depressed key whereupon the key coupler 55 restores the keys to their normal undepresed position, which through the cam slots 59 and rods 59, I04 and I26, restores the segments 60, 11, 10, 19, and I and the totalizer actuators 10, H and 13 to their normal positions.

The mechanism for rotating the totalizer engaging cams 96 and 91 will now be described.

A spring-pressed pawl 99 (Fig. 9), pivotally supported on a drive arm I05 fast on the rock shaft 90, cooperates with one of a pair of opposed recesses I06 and I01 in the periphery of a disk I06 secured to the cams 96 and 91. The shaft 90 and the drive arm I05 are given one invariable rocking movement, first in a counter-clockwise direction and then in a clockwise direction, as viewed in Figs. 7 and 9, at each operation of the machine, by a tooth drive segment I09 carried on the forward end of an arm I I0 fast on a shaft III secured to the key coupler 55 in axial alignment with the pintles supporting the key coupler.

To prevent torsional strain on the shaft III, a tail II2 on the arm IIO extends rearwardly and downwardly where it is slotted to embrace the coupling bar 56 of the key coupler 55. The segment I09 meshes with a partial gear II3 (Figs. '1 and 33) fast on the rock shaft 96 and having fast to the side thereof a mutilated disk III. A spring-centered pawl II5, pivoted on a stud projecting from the intermediate frame 88 cooperates with a serrated section of the periphery of the disk Ill to form the usual full-stroke device.

Depression of a key, or keys, rocks the key coupler 55 (Fig. 7), the tail II2, the shaft III and the segment I09 clockwise to rotate the partial gear H3 and the shaft 98 counter-clockwise through slightly more than 180 degreesof movement. The shaft 98 carries the drive arm I05 (Fig. 9) and coupling pawl 99 therewith, picking up the recessed disk I00 and rotating it and the cams 96 and 91 counter-clockwise exactly 180 degrees of travel, to first engage and then disengage the totalizer with the actuators, as described above.

Means is provided to prevent over rotation of the cams 96 and 91 at the sudden stoppage of the key coupler 55, segment I09 and drive arm I05, at the end of the downward stroke of a key. This means includes a device operated by the key coupler to stop the cams at exactly one-half rotation. The shaft 98 completes its counterclockwise rotation at the instant the depressed key reaches the limit of its downward travel.

As the cams 96 and 91 rotate, a stud II6, projecting laterally from the face of the cam 96 strikes the lower edge of a restraining pawl II1, pivoted on a stud II6 projecting inwardly from the intermediate frame 69, displacing the pawl upwardly against the tension of its spring II9, which, as soon as the stud H6 is past the nose I20 of the pawl, restores the pawl to its normal position wherein the nose I20 rests in the path of the stud H6 to prevent retrograde movement of the cams 96 and 91 and of the disk I08. The downward movement of the pawl H1 is limiting b a finger I2I on the pawl striking a stud I22 projecting horizontally from the intermediate frame 69.

As the stud II6, near the end of the down stroke of the key, passes the nose I20 of the pawl Il1, it strikes an arcuate face I23 of an arm I26 of a lever I25 (Figs. 3 and 7) fast on the key coupler shaft III, the face I23 being moved downwardly into the path of the stud II6, as the key coupler 55 is rocked upwardly by depression of a key. A stud I26 located diametrically opposite the stud II6 moves from beneath the lower tip of the elongated face I25 before this face arrives in the path of the stud I I6. The stud I26 is exactly like the stud II 6 and is necessary because the cams 96 and 91 are symmetrical and do the work in one-half rotation normally done by a cam in a complete rotation.

When the operator releases the key at the end of the downward stroke thereof and the weight of the key coupler 55 restores the keys to normal, the segment I09 rotates the partial gear II3, the shaft 96 and the drive arm I05 clockwise, the pawl 99 (Fig. 9) travels over the periphery of the disk I08 until the nose of the pawl drops into the recess I06. 0n the restoring movement of these parts the cams 96 and 91 are held against restoring or clockwise movement by the pawl I I1.

Thus, it can be seen that the oscillating movement of the rock shaft 98, by the drive arm I05 and pawl 99 turns the cams 96 and 91 one-half rotation at each operation of the machine, which, due to the configuration of the cams rocks the totalizer frames 85 and 86 first to engage, and then to disengage the totalizer with the actuators 10, H and 13.

Indicators The machine is provided with indicators to display the amounts registered in the machine toward the front and also toward the rear of the machine.

Indicators of the "roller type are substituted in the present machine for the target indicators usually provided in machines of this type. The advantages of the roller indicators as over the target indicators are that they can be manufactured at considerably less expense and they permit the indicators to appear in the proper relation.

There are two indicators for each denominational group of keys, the two being operated in unison, one to display the value of the depressed key toward the front and one to display the corresponding set-up toward the rear of the machine. The indicators are of the type disclosed in Letters Patent of the United States, No. 1,812,020, issued to William H. Robertson on June 30, 1931. These indicators are resiliently set in both directions to eliminate the torsional strain or shock occasioned by the rapid rotation of the indicators, especially when a 9 key is depressed with the indicator for that group of keys standing at zero" or "one, and vice versa, when the "one key is depressed and its indicator is standing at 8" or 9. The resilient indicator drive is not shown in the drawings of this case, but for a full understanding thereof, reference may be had to the above-mentioned Robertson patent.

A description of the setting of the indicators for the tens of cents bank will serve as illustrative for those of the other banks. The indicators are set by a minimum movement device, including a segment I30 (Figs. 3 and 5) pivoted on the rod 6|, and an actuator therefor. The segment I30 has aligning teeth formed on the periphery thereof with which an aligner finger I 3|, yoked together with other fingers (see Fig. 2) and fast on a shaft I32 supported in the machine side frames 29 and 30, cooperates to align the segment I30 in the position to which it is moved. The segment I30 is set under the control of differential segments 60 by depression of a key 45.

A pair of companion links I33 and I34 (Fig. 3) curved outwardly to form a clearance opening therebetween for the rod 6I, are pivoted at their lower ends on a bail I35 carried by and connecting a pair of swinging arms I36 and I31 pivoted' on studs I38 and I33 projecting inwardly from the intermediate frames 85 and 89 respectively.

The lower ends of the companion links I33 and I34 are hubbed together and their upper ends, normally hooked over the rod 6I, are connected by a stud I40. The two companion links are laterally spaced apart to embrace there-between a denominational group of parts comprising a differential segment 60 and an indicator setting segment I30.

The connecting stud I40 on the companion links I33 and I34 passes through a cam slot I4I formed. in the differential segment 50, and also through a heart-shaped opening I42 formed in the indicator setting segment I30.

Inclined cam slots I43 and I44 formed respectively in actuator arms I45 (Fig. 3) and I46 (Fig. 4) fast on the shaft I I I and properly spaced apart thereon, embrace studs -I41 and I48 projecting laterally from the lower ends of the swinging arms I36 and I31 respectively.

Depression of a key or keys, rocks the key coupler 55 and shaft III clockwise, carrying the actuator arms I45 and I46 therewith, thereby camming the bail comprising the rod I35, arm I35 and arm I31 clockwise about its pivots I38 and 39 to shove the companion links I33 and I34 rearwardly. At this movement the stud I40 travels in the cam slot HI and the opening I42, and at the same time the differential cam slot 58 of the particular key depressed sets the segment 60 accordingly. The angle of the cam slot MI in the segment 00 is such that as the stud I40 moves rearwardly therein it shifts the setting segment I30 from the position it occupied at the beginning of the operation, to its new position as determined by the value of the particular key depressed; or if no key is depressed in that denominational group, the stud I40 traversing the slot I with the segment 60 for that bank standing at zero, restores the setting segment I30 to its zero position.

As the actuator arrives at the outermost limit of its travel, it thrusts a pointed nose I40 on the end of the link I33 into a particular one of a series of serrations, determined by the particular key depressed, on an arcuate bar I50 securely mounted on rods I5I and I52 extending between the brackets 15 and 16 to positively align the companion links I33 and I34, the differential segment 60 and the indicator setting segment I 30 at the instant the actuator arrives at its outermost point of travel.

It is to be remembered that the groups of keys for the pennies and dollars banks are each provided with a similar arrangement for setting their indicators.

Setting segment aligner One of the features of the instant invention is the adaption of the well known ro1ler" type indicator to a machine of the "press down key type. This is made possible by employing a novel aligning mechanism to positively align the indicator setting mechanism the instant said setting mechanism arrives at its new position and before the momentum of the resiliently set indicators can displace the setting, and which positiveiy holds the aligners in engagement with the setting mechanism to prevent the backlash or whip from displacing the set indicators.

This novel aligning mechanism is best shown in Figs. 3 and 4 and will now be described.

The setting segments I30 are normally locked by aligner fingers I3I engaging notches in the periphery of the segments I30. A spring I53 (Fig. 4) has one of its ends attached to an angular arm I55 of an aligner operating lever I56 fast on the shaft I32 on which the aligner fingers I3I are fast. The spring I53, urging the lever I56 and the shaft I32 to rock counter-clockwise, normally presses the tip of the other arm I51 of the lever I56 against a hook formed on a restraining arm I58 of a multiple-armed control lever I58 pivoted on the shaft I52 extending between the bracket 16 and a second bracket (not shown), which arm I58 normally restrains the lever I56 and shaft I32 in their normal positions, thereby positively holding the aligner fingers I3I in engagement with the aligning teeth on the setting segments I30.

Before the segments I30 can be moved to new positions it is necessary to disengage the aligners I3I therefrom. These aligners I3I, when freed from the arm I58, are removed from the segment notches by the spring I53. To release the aligner fingers I3I to the action of their spring I53, to permit the stud I40 and differential segment to reposition the setting segments I30, the aligner control lever I59 is rocked clockwise early in the operation of the machine by the following mechanism.

A link I6I (Figs. 3 and 4) connects an arm I62, fast on the key coupler shaft I I I, to an arm I63 of a lever I64, pivoted on the stud I39 on which the swinging arm I31 pivots. This link I6I transmits the rocking movement of the key coupler 55 and the shaft III to the lever I64, rocking this lever first clockwise and then counterclockwise to normal position.

On the clockwise rotation of the lever I64, a by-pass tappet I65, pivoted on the free end of the other arm I66 of the lever I64, strikes a stud I6'I projecting laterally from an arm I63 on the control lever I59, rocking this lever also clockwise against the tension of a spring I69 having one of its ends attached to an arm I16 of the control lever I59, to remove the hooked arm I58 out of the path of the arm I5'I. The spring I53 then rocks the lever I56, shaft I32 and aligner fingers I3I counter-clockwise to free the aligner fingers from the setting segments I36. The counter-clockwise movement of these parts is limited by the squared end of the angular arm I55 striking a collar III surrounding, and being fast upon, the rod I5I extending between the brackets I5 and I6.

As soon as the tappet I65 is past the stud I61, its spring I69 rocks the multiple-armed lever I59 counter-clockwise, the movement being arrested by the nose of the arm I56 striking and resting on the tip of the arm I51, which was moved there-beneath at the disengaging movement of the aligner shaft I32.

The setting segments I36 are now free to be adjusted to the position as determined by the particular key depressed in each of the groups of keys. As the advancing key coupler and the cam slotted actuator arms I45 and I46, approach the end of their clockwise travel, the left-hand end of a pitrnan I13 pivoted on and actuated by bail I35, strikes a stud IN on the arm I55, and rocks the lever I56 and shaft I32 clockwise to positively reenter the aligner fingers I34 in the serrations or notches in the setting segments I36. The pitman I13 is bifurcated at its left-hand end, as viewed in Figs. 3 and 4, to embrace and be guided by the rod III. As the lever I56 rocks clockwise and the tip of the arm I5'I clears the hook on the arm I58 the spring I69 restores the multiple-armed lever I59 to its effective position to positively restrain the aligner fingers I3I in their engaged position. At the very end of the depression of the key, or keys, and of the clockwise movement of the lever I64, a stud I86 on the arm I66 strikes a face I8I on an arm I82 of the lever I59 to positively move the hooked arm I58 into its restraining position with the tip of the arm I51, should the spring I69 for any reason fail to do so.

In actual operation of the machine, the tip of the pitman I13 restores the lever I56 just before the stud I36 strikes the face I8I of the arm I92, the spring I69 immediately rocking the lever I69 counter-clockwise to hook the arm I58 over the tip of the arm I5'I so that the stud I86 normally does no work, merely acting as a safety member to prevent the lever I59 from lagging or sticking, and to insure that the segments I36 are positively aligned in their set position.

When the pressure on the depressed key or keys is released, and the key coupler 55 together with the shaft III rocks counter-clockwise to normal position, the actuator cams I43 and I44 rock the bail I35 counter-clockwise to withdraw the pitman I13 and, at the same time, the link I6I rocks the lever I64 counter-clockwise to normal, the by-pass tappet I65 wiping by the stud I6'I, tensioning its spring which, immediately after the tappet clears the stud, restores the tappet to its normal position. The counterclockwise movement of the cam arms I45 and I46 through the cams I43 and I44 draws the bail I35 inwardly to restore the companion links I33 and I34 and the pitman I13 to their normal positions, as shown in Fig. 3.

The differential adjustment of the setting segments I36 rotates the indicators 38 to position them according to the particular keys depressed and, since the segments I36 are moved directly to their new positions, so also are the indicators 36 rotated from their old positions directly to their new positions without first passing through their zero positions.

A link I63 (Fig. 3) connects the setting segment I36 to an arm I34 pivoted on a shaft I95, journaled in the indicator frames 4|, to transmit the differential movement of the segment I36 to the arm I64 connected by a yoke I36 to an arm I81 also journaled on the shaft I85. The arm I81 carries a segment I88, meshing with an indicator pinion I89 journaled on the indicator shaft 46 to rotate the indicator 38 from the position in which it was left at the end of the last operation, directly to its new position, as determined by the particular key depressed, without first returning the indicator to zero.

However, before the indicators may be reset to their new position it is necessary to disengage indicator aligners I96 (Figs. 3 and 7), fast on an aligner shaft I9I journaled in the indicator frames 4|. An aligner I96 cooperates with the pinion I99 for each of the indicators. The

aligners I96 serve to hold the indicators in parallel alignment after they have been set to their new position, thereby correcting any tendency of the indicators to assume a staggered alignment due to lost motion between the setting segment I36 and the pinions I69.

A flanged by-pass cam I92 (Fig. 7) pivotally carried on an operating arm I93, journaled on the indicator shaft 46, cooperates with a stud I94 on an arm I95 fast on the aligner shaft I9I,

to rock the arm I95, shaft I9I and the aligners I96 clockwise, disengaging the aligners from the pinions I89 and restraining them in the disengaged position until the indicators are set to their new positions, and then allows the stud I94 to escape the cam 'I92 whereupon an aligner restoring spring I96 reengages the aligners I 96 with the pinions I99.

A link I91 connects the cam arm I93 to an aligner operating arm I98 fast on the operating shaft III. pressed and the key coupler 55 and shaft III rock clockwise, the arm I98 raises the link I91 to rock the cam arm I93 counter-clockwise engaging an angular flange I99 with the stud I94, rocking the arm I95 and shaft I9I clockwise to disengage the aligner I96. The short face of the flange I99 rocks the arm I95 and the longer face restrains the indicator aligners in their disengaged position for the proper duration of time, or until the indicators are set, whereupon the flange I99, continuing its counter-clockwise travel, passes from beneath the stud I94, freeing the arm I95 to the action of its spring I96, which immediately reengages the aligners I96 with the pinions I99.

At the return movement of the key coupler 55 and the shaft III, the arm I98, by the link I91, rocks the cam arm I93 clockwise to its normal position, the inner face of the short flange riding over the stud I94. The movement (in both directions) of the cam I92 is limited by, and the cam is guided by, a stud 265 projecting from the arm I93 through a concentric slot 266 in the cam I92. A restoring spring 261 restores the cam to When a key 44, 45, 46 or 41 is de- 

